Reaction and fluid lock rotary hydraulic driving unit



June 13, 1950 F. w. TORRANCE 2,511,135

REACTION AND FLUID LOCK ROTARY HYDRAULIC DRIVING UNIT Filed May 2, 19458 Sheets-Sheet l I NVE NTOR F W TOREAHL'Q HTTYS.

u 950 F. w. TORRANCE 2,511,135

REACTION AND FLUID LOCK ROTARY HYDRAULIC DRIVING UNIT Filed May 2, 19458 Sheets-Sheet 2 i am A YIIIIIIIIIIIIIIIIIIII/il INVE NTOR FWTorranceJune 13, 1950 F. w. TORRANCE 2,511,135

REACTION AND FLUID LOCK ROTARY HYDRAULIC DRIVING UNIT Filed May 2, 19458 Sheets-Sheet 5 INVENTOF? PW. Tor) nce MMK June 13, 1950 i w, TORRANCE2,511,135

REACTION AND FLUID LOCK ROTARY HYDRAULIC DRIVING UNIT Filed May 2, 19458 Sheets-Sheet 4 FIG. 4

, Q INVENTDR F W Torrance June 13, 1950 F. w. TORRANCE REACTION ANDFLUID LOCK ROTARY HYDRAULIC DRIVING uNIT Filed May 2. 1945 8Sheets-Sheet 5 FIGS INVENTOR FMTorrance y 3 June 13, 1950 w TORRANCE2,511,135

REACTION AND FLU ID LOCK ROTARY HYDRAULIC DRIVING UNIT Filed May 2, 19458 Sheets-Sheet 6 FIG. 6

INVENTOR Fla/Torrance a as g F. W. TORRANCE REACTION AND FLUID LOCKROTARY HYDRAULIC DRIVING UNIT II/l/l/Illfl June 13, 1950 Filed May 2,1945' INVE N T O R F h/Tormnce a nrrys.

FIG.8

June 13, 1950 F. w. TORRANCE 2,511,135

REACTION AND FLU ID LOCK ROTARY HYDRAULIC DRIVING UNIT Filed May 2, 19458 SheetSSheet 8 E 45a. 4 45c;

I NVENTOF? Fh/Tormnce- Patented June 13, 1950 UNITED STATES P'i'ENTOFFICE REACTION AND FLUID LOCK ROTARY HYDRAULIC DRIVING UNIT 15 Claims.

This invention relates to hydraulic driving units in which power istransmitted from a driving to a driven member by a fluid medium, and ina varied manner.

Hydraulic or, fluid drives have previously been proposed and largelywould appear to fall in three main groups: (a) Units incorporating afixedly mounted drive pump, pipe connected to a fixedly mounted fluidmotor in which any reasonable degree of torque or speed may be obtainedby the relative proportions of the pump and motor, but, in terms ofsize, high torque and high speed are not practicable in the same unitWhile a substantial loss of power results due to friction in the pump,pipes, valve and motor.

(b) Units embodying a rotary or reciprocating pump axially mountedbetween the driving and driven members, having the case connected toone, and the rotor or piston connected to the other, wherein the drivingconnection is efiected by restricting the pumped fluid, comparable inaction to the slip of a friction clutch, producing a low startingtorque, and power waste at all speeds below a direct 1 to 1 drive.

Units in which two opposed driving and driven members axially mounted ina fluid chamber, transmit power by circulation of fluid in the chamberwhich produces a low startin torque, constant slip at all speeds andconsequent heating of the fluid,

The present invention avoids such general disadvantages as noted inthese several types and provides a unit of reasonable size in which ahigh torque drive may be produced at all intermediate speeds, thedrivingv force being supplied by a combination of driving effects duringthe transitory driving range.

Of those fluid drives depending upon fluid lock, the characteristicswhich identify one from the other depend mainly upon the principlesadopted to develop a sufiicient torque at starting and in those rangesof operation intermediate of starting and fluid lock. Although theprinciple of fluid lock itself is well known. the means which have beenused to accomplish th s condition have varied widely. As to theconditions of the initial torque required, and the transitory conditionbuilding up to fluid lock, various means have been adopted in the pastwhich have involved external mechanisms to control oil pressure or theadoption of a diiierent driving principle until fluid lock is obtained.

It is, therefore, a main object of the present invention to produce asubstantially simple hydraulic drive unit which depends upon theprinciple of changingthe direction of a moving body of oil and derivingenergy therefrom to produce a high rqu at w a d n ermedia e speeds andwhich further dependsupon increasing the resistance to flow of the oilto diminish the relative rotation oi the shafts and untimate- 1y fluidlock.

Another object of the invention is to produce a substantially simplehydraulic drive which will produce a high torque drive in lower. speeds,and a fluid locked drive at higher speeds, and which will operateefficiently at. all speeds,

A further object oi the invention to, pro.- vide a unit of this kindwhich is controlled automatically during operation, will engage. anddisengage quickly and completely under all conditions and may becontrolled by simple connections to common operating media.

A further object is to provide a unit of, this character automaticallycontrolledby a governor in relation to the speed including control ofcentrifugal forces to produce a fluidtight unit with provision forselective normal governor control to produce other eifects such as afree wheeling effect.

A still further object of the invention is to provide a self containedhydraulic drive unit of generally simple construction which lends,itself to production line assembly and which may be employed in manyfields.

With these and other objects, in view the in vention generally,comprises a unit incorporating an impeller driven by a drivev shaftfroma source of power, an expansible chamber pumping unit housed within theimpeller, one pumping component of which forms a partof the impeller,and a runner fastened to a driven or output shaft. The runner includesan inner movable vane structure of generally annular form extendingabout a portion of the impeller and having passages of spiral-likenature extending radially therethrough in a direction opposed to thedesired direction of movement of the runner. The impeller has vanemembers defining passages in conjunction with the vanes. of the runnervane structure to provide communication of fluid from the pump to theperiphery of the runner vanev structure. A runner ring constitutes theperipheral portion of the runner and has a plurality of passagesdesigned to be aligned with passages of the runner vane structure nearthe peripheral zone of the latter in one position of relative adjustmentof the runner vane structure within the runner. Suitable means areprovided for causing the runner vane structure to move within the runnerand its runner ring to cause the passages of the runner ring to move outof alignment with passages of the runner vane structure to shut off flowof fluid through the unit. The unit therefore, not only operatesaccording to conventional fluid lock principles in conjunction with itspumping mechanism but also derives driving effect in the transitoryrange up to fluid look by fluid friction coupled with the effect derivedfrom displaced momentum of the fluid employed in the spiral-likepassages of the runner vane structure. The invention includes variousmeans of control for the practical application of the principlesinvolved, details of which including the construction and operation,will be understood by reference to the followin detailed specificationtaken in conjunction with the accompanying drawings.

In the drawings:

Fig. l is a side elevation of the transmission casing of a vehicle, thecasing being partly broken away to show part of the driving unitaccording to the present invention and some of its operative partsincluding the feed line from the fluid sump of the casing.

Fig. 2 is an end elevation of the driving unit of the present inventionshowing part of the transmission casing, half of the wall of the runnerbeing eliminated to show underlying parts of the unit.

Fig. 3 is a transverse section taken through the driving unitsubstantially along the line 3--3 of Fig, 2 and also illustrating aportion of the surrounding transmission casing.

Fig. 4 is an enlarged fragmentary sectional detail taken substantiallyalong the line 4-4 of Fig. 3 and showing part of the impeller vanestructure broken away tov illustrate the underlying construction of therotor vane structure, the impeller vane structure being shown in aposition where the grooves thereof are aligned laterally with thegrooves of the runner vane structure.

Fig. 5 is an enlarged fragmentary perspective view showing the runnervane structure in spaced relation to the impeller vane structure toillustrate the general structure of each and their corelation.

Fig. 6 is a fragmentary section taken substantially along the line 6-6of Fig. 3, showing the spiral oil feeding passages to the pump andillustrating the vane structure in a different position to that shown inFig. 4 so as to illustrate also the general location and arrangement ofthe grooves in the runner vane structure which are shown in dottedlines.

Fig. '7 is a transverse section taken substantially along the line 1-1of Fig. 4 illustrating in particular the inward projection of the web ofthe impeller in contact with the pump rotor as well as other details.

7 but illustrating valve in closed position shutting off fluid feed fromthe sump but opening the feed passages to the atmosphere.

Fig. 10 is a sectional detail of the breather pipe construction enteringinto the oil sump.

Fig. 11 is a transverse sectional detail taken through the runner casingand runner vane 4 structure illustrating the mounting of the cranks usedin conjunction with the governor arms for shifting the position of therunner vane structure.

Fig. 12 is a sectional detail taken through part of the impellerstructure showing the manner in which the side walls of the impeller arebolted to the projecting vane structure thereof.

Fig. 13 is a fragmentary sectional detail taken through the runner vanestructure indicating the manner in which the two parts thereof may besecured together by bolting.

Fig. 14 is a fragmentary section taken through the runner housing andthe runner vane structure showing an alternative manner of securing thewalls of the runner together at one side of the unit.

Fig. 15 is a, fragmentary detail section taken substantially along theline l5|5 of Fig. 3 to illustrate in top plan view the opening throughthe rotor vane structure discharging from the fluid channels.

Fig. 16 is a fragmentary longitudinal section taken through the runnerring and the outer portion of the runner vane structure illustrating thepath of discharge of fluid from the runner vane structure through therunner vane.

Fig. 17 is a similar view to Fig. 16 but illustrating the runner vanestructure rotated to position to shut off communication between thechannels of the rotor vane structure and discharge slots of the runnerring.

Fig. 18 is a transverse sectional view taken through the runner ring atone of the points where the channels of the runner vane structure openon the surface thereof and illustrating the shape of the recessedportion of this structure adjacent the outlet of the channel forgradually restricting the area of the discharge slots in the runner ringas the runner vane structure is rotated relatively to the latter.

Fig. 19 is a fragmentary side elevation of the controls operated by theaccelerator pedal and brake pedal respectively to place the transmissionunit in communication with the oil sump or to shut it off therefrom andmeans of varying the effect of the governor control through operation ofthe brake pedal; and

Fig. 20 is an enlarged fragmentary side elevation of a connecting meansfor varying the operation of the governor to require a greater rotorspeed for the closing of the ports in the rotor ring to permit morepower for special condition.

The invention is aptly illustrated by Way of the transmission of a motorvehicle wherein A indicates the casing of the transmission from whichthe driven shaft [0 projects. This is suitably journalled in the casingas shown in Figs. 1 and 3 including the aligning bearin 11 and packingglands l2 and Ho and retaining ring I212. The driven shaft passes intothe fluid transmission unit generally indicated by the letter B and isconnected by the spline l3 (Fig. 3) with the runner C so that uponrotation of the runner the driven shaft will rotate correspondingly.

The runner C is caused to rotate in normal driving conditions, as aresult of a fluid driving connection between the impeller D and therunner C, the impeller being initially rotated by means of the splinedhub or stub shaft M which is in direct driving connection with the crankshaft of the engine. The impeller is generally comprised by acylindrical casing formed by spaced apart side walls l5 which securetherebetween and include the peripherally projecting impeller vanestructure having. vane surfaces It forming side walls of spiral passagesI? (Fig; 3) more detailed references to which will, be had hereinafter.

Inwardly of the impeller vanes and between the side walls [5 of theimpeller casing, a pump chamber I8 is formed of. substantiallycylindrical contour. This is designed to house the cylindrical pumprotor E splined on driven shaft Ill and provided with a plurality ofradially directed blades l9 spring pressed outwardly by the compressionsprings and normally projecting from the'periphery of this rotor. Theseblades are chamfered along one edge and are designed to make closecontact with the inner. edge of a web 2| projecting inwardly from theimpeller vane structure'which edge is eccentric relative to theperiphery of the pump rotor E and carries the opposed laterallyextending arcuate plates or shoes 22, the inner surfaces of which areflush with the edge of the web. The plates or shoes 22 arecircumferentially spaced apart from one another to provide therebetweenport areas 23 (Figs. 4 and 6). Consequently, in initial stages ofoperation, 1. e. during rotation of the impeller, and non-rotation ofthe runner C and pump runner E the plates or. shoes 22 rotating aroundthe pump rotor E eccentrically thereto and engaging the bladesI9'thereof will. obviously create a partial vacuum condition which willcause the fluid to be sucked from the sump of casing A into the pump andto be discharged through the ports 23 to the distribution chamber 24divided centrally by projecting web 2| as will bedescribed in moredetail hereinafter.

Let us assume that the impeller D is caused to rotate by the crank.shaft of the vehicle. In this instance pumping action will immediatelystart as above referred to as soon as the motor turns over. However thefeed of the driving fluid from the sump of the transmission case A iscontrolled by the accelerator pedaland, unless theaccelerator pedal isdepressed, air only will be drawn into the transmission unit B. Forinstance, upon referring to Fig. 1 the fluid intake pipe communicatingwith the fluid sump 28 is controlled by a valve operated by thetransverse shaft 2! (see Figs. 1 and 3). This latter shaft, as shown inFig. 3 has an end 28 which projects outside the casing A. Suitableoperating connection, therefore, may be made with the accelerator pedalfrom the projecting end 23 of this shaft and, by any suitable springmeans, this shaft is normally located so that the valve which it rotatesshuts off communication from the sump 2% and opens the oil feed passageto atmosphere. In this connection reference is made to Figs. 8 and 9.

In Fig. 9 the valve 29, formed with the feed passage 39, is disposed inthe normal position of shaft 2! and passage 39 communicates through aport 3| with the atmosphere. The intake pipe is therefore cut off fromthe feed passage which leads to the fluid transmission unit, whereas,the port 3| is placed in communication with. the fluid intake passage 32by means of a suitable bypass 33. Therefore, in the initial stages ofoperation when the motor is running and idling, the pump blades 49operating in pump rotor E will only cause intake of air. If, however,the accelerator is depressed, its operation of the shaft 2'! will causethe latter to rotate and in turn rotate the valve 29 to the positionshown in Fig. 8 wherein the port 30 is placed in communication with theintake pipe 25. The air port 3| is thus out 01? and therefore thefluid-feed-passase, 32. is placed. in, direct communication, with. thefluid sump 26 via, intake pipe 2-5and valve feed pas.- sage '30. As aresult, therefore. fluid: will be drawn through the intake 25 and passedto the. feed passage 32.

The driven shaft H), as will benoted from Fig. 3 particularly, is formedwith a hollow bore 34 over a portion of its length, closedat one end bythe plug 34a and provided towards the otherend with an enlargement 35which is radially bored as at 36 to provide a plurality of radialpassages leading into the bore 34. The radial passages 36 open into thefluid feed chamber 31 with which the fluid feed passage 32 communicates,so that fluid. is therefore fed from the sump and through the bore 34 tobe discharged through the series of openings 38- (Figs. 3 and 7) in thedriven shaft as it extends within the fluid transmission unit B. Thesepassagesarelocated to discharge the fluid, into thereceiving chamber 39of the impeller D (Figs. 3 and '7) the fluid being transferred from thischamber via the spiral passages 39ato the periphery of the pump rotorwhich latter element includes side plates 3% and pressure equalizingpassages 39c (Figs. 3 and 4' respectively) The main body of the.impeller (vane structure) in longitudinal section between itssid'e walls15, takes the form of an annular member having its outer peripheryindicatedby the numeral til and its inner, periphery indicated bythenumeral 4| (see Figs. 4 and 6). This constitutes a solid body having aplurality of; spiral passages 81 therein open throughout their extent onits side surfaces, to which reference presently will be had, and theinner periphery M of this member together with the side walls I5 of theimpeller constitute the distribution chamber 24.

The spiral passages I! are formed in this annular member inwardly fromeach thereof, d vided by the partition web 2| which, as previouslyindicated, extends inwardly beyond the inner periphery M (Fig. 4) toterminate in an edge disposed eccontrically to the periphery of the pumprotor E and carries at this point, as previously referred to, theopposed spaced apart arcuate plates or shoes 22. The spiral grooves orpassages I! as will be notedboth from Figs. 3 and. 4, extend, from thedistribution chamber 24 to the. outer periphery 40 of this annularmember and, therefore provide in each instance, a series of pairs ofpassages divided by a partition and located at uniformly spaced apartintervals throughout the circumference of the member. Qonsequently, asfluid is pumped to the distributlon chamber 24, itv is discharged fromthere into the grooves or passages I! on each side of the web 2| and,due to this continuing pumping action, and, the effect of centrifugalforce caused by the rotating impeller body, the fluidis caused to passthrough these passages and is discharged therefrom into a series ofsubstantially corresponding passages (later described) provided in therunner structure C from which itis discharged in the initial stages ofoperation to cause rotation of the runner in the same direction as theimpeller hereinafter referred to in detail.

The casing of the runner C, as will be seen upon reference to Figs. 3and 7 particularly, is made up of annular sidewalls 42 terminatingv attheir outer peripheries in a runnerring 43 which, in effect, provides asubstantially enclosed casing. This structure may be produced by forming1| the walls, 42, at their outer peripheries, with a laterally inwardlydirected flange, the two parts being bolted together to form thiscasing. Within the casing thus formed a runner vane structure 44 isprovided and encased adjacent the outer periphery of the casing.

This structure is preferably made up of a plurality of arcuate sectionsor segments 45 (Fig. 4) which are slightly spread apart from each otherat the ends and held in this relation in suitable manner such as by thecompression springs 46 which will permit heat expansion. The assembledsections or segments 45 provide a runner vane structure 44 of annularform which is preferably formed longitudinally in two annular halves,for

assembly purposes, secured together so that each complete assembledsegment 45 is made up of two pieces 45a and 45b (Fig. 11). Each of thesepieces is cut inwardly from its inside surface 41 (Figs. 7, 11 and 14)to a point adjacent to its outside surface 48 to form a plurality ofspiral passages or grooves 49 spaced apart circumferentially of the unit44 thus forming the vane surfaces 49a curved coincidentally to the vanesurfaces I6 of the impeller D. The inner side surfaces 41 of parts 45aand 45b are recessed or chamfered to form when these parts are assembledtogether as segments 45, the channel 450. The channel 450 is of acontour in cross-section, corresponding to the cross-sectional outlineof the peripheral portion of the impeller vane structure, to house thelatter (Figs. 3, 7, 11 and 14) so that it may rotate therethrough, therebeing at least a practical working clearance between the peripheralparts of the impeller and the edges of channel 450 of the runner vanestructure.

The grooves or passages 49 of the runner vane structure 44, open intothe channel 450 and therefore it will be clear that as the impeller Drotates relatively to the runner vane structure 44, in initial stages ofoperation, the passages I! of the impeller will intermittently becomealigned with the passages 49 of the runner vane structure 44. Moreover,it will be noted that the runner ring 43 is provided with spiral slots50 of a curvature corresponding or substantially corresponding to thatof the grooves or passages l1 and 49 and consequently when the lattergrooves are aligned or substantially aligned with the slots 50, a freedischarge of fluid from these grooves to the exterior of the ring isproduced during operation.

Initially when starting or at slow speed the fluid might not flow asreadily as desired from impeller grooves IT to the runner vane groovesdue to the rotation of the impeller D relative to the stationary orslowly moving runner C. Accordingly therefore ring like by-passingchannels (Figs. 2, 3, 4 and 6 and 14) are formed in the inner surface ofthe wall of the runner and disposed inwardly of the inner periphery ofthe runner vane structure 44 so that fluid passing outwardly in thegrooves I! of the impeller D will pass into these ring like channels 5|and therefore it will be freely fed to the grooves 49 of the runner vanestructure 44 which intersect these channels. wardly through the groovesor channels 49 by reason of the action of the pump and, centrifugalforce of the rotating impeller, to be discharged through the slots 50.

The spiral grooves l1 and 49, as well as the spiral slots 59, are, aspreviously indicated, uniformly spaced apart around the circumference ofthe transmission unit and spiral outwardly from the center thereof,inclining rearwardly in It will then, of course, pass outi quently fluidis discharged, in a direction rear wardly to the direction of rotation,in a plurality of jets.

Surrounding the runner C is the stator ring 52, attached to thetransmission casing by studs 52a (Figs. 2 and 6) which is formed with aseries of channels 53 on its interior surface, the channels being formedas to provide a means of conducting oil, being disposed directly in thepath of the jets of fluid which discharge through the series of slots 50in the runner ring 43.

The slots 5|] in the runner ring and the grooves 49 in the runner vanestructure correspond in number as well as general profile while thegrooves IT in the impeller vane structure of the same general profile,may be of the same number although not necessarily. Preferably a greaternumber of grooves IT in the impeller are employed as compared to thenumber in the runner vane structure 44, to eliminate possibility ofvibratory effects as the grooved portions ll of the impeller pass thoseof the runner vane structure. Any desired practical number of pockets 53may be provided in the stator ring 52.

Upon rotation of the runner C, the driven shaft In is caused to rotatedue to the driving connection therebetween. Moreover, due to the drivingconnection between the pump rotor E and the driven shaft ID, the pumprotor is caused to rotate, which rotation effects a decrease in therelative speed between the pump rotor E and the impeller D and thevolume of fluid pumped starts to decrease. As the rim speed of therunner C is increased, the velocity of the fluid discharging through theslots 50 of the runner must increase correspondingly.

In order to change over operation, I provide a means for shifting therunner vane structure 44 to control the operative area of the slots 50.This is accomplished by a governor control. On the runner a plurality ofgovernor arms 55 are provided (Fig. 2) secured at one end on the crankarms 56 of a plurality of cranks 51, the crank arms 56 being suitablyjournalled in one wall of the runner as shown, for instance, in Fig. 11.The opposite end of each crank is provided with a suitable boss or thelike 58 which enters into a receiving slot 59 formed in one outer wall48 of the runner vane structure 44.

The free end of the governor arms is provided with a weight 5!! which isoperatively connected by means of a link 6|, in each instance, with alug 62 carried by a control ring 63 (Fig. 3) which is rotatably mountedon an enlarged portion 64 of the runner housing. This provides foruniform operation of the governor arms. On each of these arms by anysuitable means such as a lug 65, the governor arms are operativelyconnected with compression springs 56 preferably carried upon an arcuateguide support 61 which is anchored at one end, in each case, in a lug68. The compression spring 66 is carried on the support 6! between thelug 55 of arm 55 and a suitable restraining washer 69 carried on the endof support 5?. Consequently as the runner rotates and the governor armsare caused by centrifugal force to swing outwardly against compressionof springs 66, their crank arms 56 will be rotated to a correspondingdegree and consequently each crank will be turned in its journal so thatthe boss 53 of each crank, operating in the slots 59 of the wall 48 ofthe runner vane structure 44, will cause the runner vane structure topartially rotate, thus displacing the terms of the direction of rotationand conse- .75 grooves or channels 49 from their direct registry withthe slots 50 of the runner ring 43. Ordinarily, in this case, if onlythe grooves 49' were provided, communication between the grooves 49 andthe slots 50 would in effect, be cut off. It should be noted, however,that on the outer periphery of the runner vane structure, directlyadjacent to each groove 49, a recess 16 is pro- Vided of a shape such asillustrated in Fig. 18, having the converging side walls a. or of suchother shape as to provide for a gradual restriction in effectivedischarge area of the slots fail to cause an increase in velocity of thedischarging fluid. Thus, as the runner C gradually picks up speed, thearea of the slots 70 becomes correspondingly smaller until the runnerhas attained the speed of the driving shaft when communication is shutoff between slots 5!) and grooves 49 at which time the fluid within thegrooves 49 looks the 'pump'rotor and the impeller as a unitary drivingelement.

Upon decrease of power relative to the driven load, or increase of loadrelative to the available power, under normal conditions, the rotativespeed of the unit will decrease and the governor arms 55, underpressure-of their springs 66, will cause the runner vane structure 44 tomove back toward normal starting position, as a result of the movementof the cranks =61. Therefore, communication will again be establishedbetween the slots 50 and the recesses 1-0 together with grooves '49 inthe runner vane structure 44. This governor action will automaticallyadjust the necessary torque-speed ratio between the available power andthe existing load. The speedof the driven shaft can therefore beincreased or decreased, within the capacity of the unit, and availablepower, in a smooth and sensitive manner, by merely depressing orreleasing the accelerator pedal to give the desired result.

As the effective area of the slots 50-gradually lessens due to thegovernor control of runner vane structure 44, upon increase in-speed ofthe runner, and as the relative speed between impeller and therunner'decreases, the fluid, flowing directly between the impeller vanesand the runner vanes, introduces adriving effect which I term a vanedriving efiect due to gradually increasing fluid friction andcentrifugal force which imparts an inertial force to the fluid. Moreoverit will be apparent that the pump-E initially has'but littledrivingfunction but, as the fluid pressure increases, it gradually operates asa driving element due to the restriction in flow of the fluid throughthe pump, as the slots 5!? are reduced in area, which gradually producea fluid locking effect, until finally the slots 58 are closed when acomplete fluid lock occurs providing a direct drive for normal driving.

Consider the sequence of the effects causing driving forces during thetransitory range and the manner in which they overlap. When theaccelerator pedal is depressed, the unit B is caused to fill with fluidas previously explained, thus producing the initial driving effect. Asthe runner begins to gather speed the displaced momentum effect and vanedriving effect begin to rise. Thus as the runner continues to gain'speedthe two forces build up each contributing to the resultant torque untilfinally, as the runner speed reaches about seventy-five percent of itsspeed in the transitory range, the fluid locking means of fluid lockingwhich becomes the main driving begins to close gradually producing acondition force, continuing with increasing eflectiveness until acomplete fluid lock is reached at which point the movement of the rotorvane structure 44 has reached its maximum and closed the ports 50 in therunner ring 63.

It will be noted that the vane driving effect contributes little at lowspeed in the transitory range but as the fluid is restricted by the movement of the runner vane structure M with consequent restriction of theports 56' in the runner vane 43, pressure is built up which increasesthe resistance between the impeller vanes and runner vanes thusproducing an increased vane driving effect which increases as ports fillreduce in area producing a gradually effective and finally completefluid lock between the impeller D and sump E.

The flow of the fluid through the driving unit from the sump, and itsdischarge through the slots til of the runner ring when in communicationwith the grooves 49 of the runner vane struc-- ture 44, is continuousand cyclic by reason of the fact that the sump is maintained with asubstantial volume of fluid and the fluid discharging through the slotstill, to impingeagainst the channel surfaces 54 of the channels 53 ofstator ring 52, is discharged from :thestator ring by means of thedischarge ports ll, the opening on the sides of. the driving unit Bbetween the outer periphery of the runner C and the inner periphery ofthe stator ring 52' the ports being formed by leavingopen the pockets53' at each side of the driving unit 13. Consequently the fluid. afterimpinging upon the surface of the pockets 53 is discharged laterally ofthe driving unit through the ports H to return by gravity to the sump'26. Moreover, it will be appreciated that the unit is consequentlylubricated fully, as external parts will be readily lubricated by thisdischarge of the fluid (preferably oil) while'internal parts obviouslyare likewise well lubricated. Furthermore, in respect to pressurewithin-the driving unit, caused by the fluid, suitable relief valves 12are preferably incorporated (see Fig. 3) which may be placed incommunication with the fluid by-pass rings or channels iii. A suitablefluid inlet pipe 26a is preferably provided to introduce fluid to thesump 26 and this is conveniently closed by the breather cap- 26Bwhichmay be formed with a rod 260 carrying the opposed spring like members2603. The sump 26 may therefore readily be maintained with sufficientvolume of fluid.

It is preferable to provide for manual operation of the governor arms toproduce substantial advantages and this is provided for in the presentinvention. In this case the lugs '68 to which the guide rods '61 areanchored, take the form of bell crank levers-indicated generally by thenumeral ltwhich are suitably pivoted on brackets 74 carried on therunner casing, one arm-of the levers being constituted by each lug 68,the other arm projecting substantially at right angles thereto and beingindicated by the numeral'i fi. Thearms 15 of these levers73, in thepresent illustration, are designed to project through slots iii in thecontrol ring 63 and are disposed in the path of the flanged portion "llof the pressure applicator plate 78 which is freely mounted on theprojecting sleeve 79 of the runner C. This plate is designed to beengaged by a suitable thrust bearing 8!] slidably mounted on the'sleevel9 which bearing is in turn engaged'by the-thrust plate 8 l likewisefreely mounted onthe sleeve .19.

The thrust plate 8! preferably includes suitable lugs 82 pivotally toreceive the depending arms 83 (Fig. 2) of the transverse shaft 84 (Figs.1,;

and 18). This shaft projects outside the casing A and is designed toconnect with a lever arm 85 (Fig. 19) which is operated by theconnecting link 86 from the brake pedal. As a result, therefore,depression of the brake pedal to a substantial extent, that isapproximately to its full extent, moves the thrust plate 8| axially onsleeve I9 due to the consequent rotation of shaft 84 and the swinging ofits arms 83. Movement of thrust plate 8i inwardly will frictionallyengage the facing surface 81 of control ring 93, thereby retardingrotation of control ring 63 in relation to the runner C with consequentretraction of the governor arms 55 against the centrifugal force ofgovernor weights 69 through the connection of links 6|, attached togovernor Weights $0, and control ring 63. In this operation these armswill be retracted to their full extent causing the portsv 50 to be fullyopened. This action is effected without the use of the applicator plate18 and the arms employed for manual retraction of the governor arms,manual operation of the latter being omitted where desired.

As a result of this retarding action, a free wheeling principle may beestablished. For instance, upon releasing the accelerating pedal whichthen cuts off the source of fluid supply to the driving unit, bypositioning valve 29 as shown in Fig. 9, and upon pressing the brakepedal to substantially full extent momentarily, the action justdescribed will result causing the runner vane structure to return tonormal starting position, establishing full communication between theports 50 and the grooves 49 of the runner vane structure so that thefluid will be completely discharged from the driving unit B almostinstantly. The release of the brake pedal will permit the governor toclose passages 49 from communication with ports 50 and, as the fluidcontact between driving and driven parts of the unit is removed,coasting or free wheeling results. However, reinstatement of normaldriving conditions are readily achieved merely by pressing again uponthe accelerator pedal to place the fluid driving unit again intocommunication with the fluid feed.

In stopping a vehicle employing this driving unit, a substantiallysimilar action will take place except that the vehicle brake is used asneeded by depressing the brake pedal to the required degree, and for therequired interval, to stop the vehicle. In this case the engagementbetween the thrust plate BI and the facing surface of the flange 81 ofcontrol ring 63 supplements the braking action in effect to give thesupplementary speed retarding action supplied by the ordinary vehicletransmission While its clutch is engaged. The meeting faces of thethrust plate 8! and the control ring 63 may be given frictionalcharacteristics if desired. It might be noted at this point also thatmore power may be developed for special conditions by partial depressionof the brake pedal without causing engagement of these faces as will bereferred to hereinafter.

As indicated previously, the driving unit B during idling, is open tothe atmosphere to permit air only to be drawn therein and, is placed incommunication with the oil sump to admit fluid only when the acceleratorpedal is depressed. One preferred means of effecting this operation isby employing, as shown in Fig. 19, a cam lever 88 pivotally connectedwith the link 39 connected with the accelerator pedal. The cam lever 88is provided with the cam surface 89 and one edge of this lever, in thenormal position, is designed to abut the roller rotatably carried on thearm 9| which is fastened to shaft 21 exteriorly of the transmissioncasing A. As a result, therefore, the depression of the acceleratorpedal will cause the abutting edge of lever 88 to swing the arm 9| intoengagement with its roller 90 so as to rotate shaft 21 in a clockwisedirection, thus to establish communication by port 30 of valve 29between the sump and fluid feed passage 32, as shown in Fig. 7, movingit from the idling position shown in Fig. 8. Moreover, as theaccelerator pedal is depressed to an increasing extent the cam surface89 of the lever 88 will come into engagement with roller 90 and maintainthe arm 9| in its downward position as shown by means of the dotted lineillustration of roller 90 (Fig. 8). Therefore, in all positions ofdepression of the accelerator pedal the arm 9| will be swung from thenormal and will establish, by port 36, communication between sump pipe25 and fluid feed passage 32.

Provision is also preferably made for the manual regulation of thegovernors by increasing the resistance of the compression springs 66against the governor arms 55. This may readily be accomplished by anysuitable lost motion connection and one suitable arrangement is shown inFigure 20. In this construction an operating link 92 is suitablyconnected with the applicator plate 18 so that axial movement of the rod92 in one direction will cause the applicator plate to depress the arms15 of the lever 13 and to pull the supporting guide 6'! inwardly withconsequent retraction of the governor arms 55. Thus, if by this means,the pressure of the coil springs 66 relatively to the normal operatingposition of the arms 55 of the governor is in effect increased, it willrequire a greater rotational speed of the runner C to return the arms 55to normal driving position and thus permit the closing of the ports 59.This will therefore permit more power for special conditions.

Operation of the link 92 may be effected by means of a rod connection 93to the foot pedal and/or a rod connection 94 to a hand lever. In thepresent Fig. 20 showing the rod connections, rods 93 and 94 formed withthe eyelets 95 and 96, are designed to slide on the connecting link 92.In each instance, a suitable stop member, such as a cross pin 9'! in thecase of rod 93, and pin 98 in the case of rod 94, is carried on theconnecting link 92. Therefore, by reason of the lost motion permitted bythe sliding eyelet connection between the rods 93 and 94 and theconnecting link 92, the springs 66 may in effect have their compressionratio relatively to the arms 55, increased upon a predeterminedoperation.

From the foregoing it will be appreciated that by a relatively simple,generally self-contained structure I am abie to provide a driving unitwhich will provide a fluid locked drive under normal driving conditions,a high torque drive at lower driven speeds, and a drive which willquickly react and operate efficiently at all driving and driven speeds.

Moreover, it will be apparent that two driving effects are combined inthe unit, each varying in accordance with the speed of the runner C andthe discharge area of the slots 50 as controlled by the governor. Since,the vane driving effect is of little consequence until fluid resistancereaches a substantial value, the main driving force at low speeds isthat derived from displacing oil from a straight path by curving thechannels through which it flows in the sides of games '13 the runner C.As soon as the governor acts to close the ports 56, this driving effectis reduced in proportion to the opposite effects of increasing speed ofthe runner and decreased velocity of the oil due to increase in frictionand is reduced to a zero quantity at fluid lock.

There is thus a transition to a fluid locking effect which results in alocked, direct fluid drive upon fln'al closing of the slots at apredetermined speed by relative movement of the runner vane structure'44 to the runner ring 43. Finally, the unit provides for increasedpower for special conditions and readily also permits the efiect of freewheeling by a simple operation to drain all fluid from the unit. In thislatter instance, the principle is such that the fluid is completelydrained from the unit when it comes to rest so that in starting againand idling, any tendency towards drag is completely eliminated, whichotherwise'would be the case if fluid remained in the unit.

It is, of course, apparent that changes may be effected in structurewithout departing from the principle of the invention. Moreover, whilethe invention has been illustrated in the present specification chieflyin conjunction with the transmission of a vehicle, it will be obviousthat the hydraulic driving unit of the present invention has a wideapplication.

What I claim as my invention is:

1, A hydraulic driving unit comprising an impeller mounted on a driveshaft connected to a source of power, a runner concentrically mountedaround said impeller and connected to a driven shaft, pumping meanconcentrically mounted within said impeller comprising at least a pairof components, one of which is operatively connected to said driveshaft, the other of which is operatively connected to said driven shaft,a fluid reservoir in communication with said pumping means, saidimpeller having passages designed to provide communication of fluidpumped from said fluid reservoir, by said pumping means from the latter,to said runner, means mounted concentrically about said runner anddesigned to communicate said fluid to said reservoir, said runner havinga plurality of substantially radially curved passages for communicatingsaid fluid from said impeller to said means communicating to said fluidreservoir, and closure means in connection with said runner forgradually increasing the resistance to flow in said passages of saidrunner in accordance with the increasing speed of the latter to controlthe driving effect between said drive shaft and said driven shaft duringrelative rotation between said shafts, said closure means being designedto cut off fluid flow to said reservoir to provide fluid lock in saidunit between the components of said pumping means, and direct fluiddrive between said drive shaft and said driven shaft.

2. A hydraulic driving unit comprising an impeller mounted on a driveshaft connected to a source of power, a runner concentrically mountedaround said impeller and a fluid pump rotor concentrically mountedwithin said impeller, said runner and said fluid pump rotor beingconnected to a driven shaft, web means in said impeller eccentric aboutsaid pump rotor for pumping cooperation with said pump rotor uponrotation of said impeller relative to said pump rotor, means connectingsaid pump rotor with a fluid reservoir, said impeller having passagesdesigned for communication of fluid pumped from said reservoir by saidpump to said runner, a stator ring concentrically mounted beyond theperiph cry of said runner and designed to conduct fluid from theperiphery of said runner to said fluid reservoir, said runner having aplurality of substantially radially curved passages for communicatingsaid fluid from said impeller to said stator ring, said runner therebyabsorbing the reaction energy of said fluid as it passes through saidpassages, means in connection with said runner for gradually increasingthe resistance to flow of fluid in said passage in accordance with theincreasing speed of said runner to increase the fluid friction in theunit'and hence the driving effect between said drive shaft and saiddriven shaft during the period of relative rotation between said shafts,and means for shutting off flow from said runner to said stator toprovide fluid lock between said pump rotor and said web means wherebysaid drive shaft and said driven shaft are caused to rotate together.

3. A hydraulic-driving unit as-claimed in claim 1 in which the radiallycurved passages of said runner terminate in discharge ports, said meansin connection with said runner for gradually increasing the resistanceto flow in'said-passages comprising means for restrictingthe areaof saidports upon increaseof speed of said runner, said restricting meansclosing said ports at a predetermined speed to produce fluid lock anddirect drive between said drive and driven shafts at normal drivingspeeds.

4. A hydraulic driving unit as claimedin claim 1 in which the passagesformed in said impeller and said runner for passage of fluid provide aplurality of vane surfaces, said passages of said runner terminating indischarge ports, said closure means in connection with said runnercomprising. a runner ring movable relatively to said runner and havingpassages normally registering with said ports, and governor meansconnected with said runner ring for moving the latter as the runnerspeedincreases, flnally to move said passages out of registry with saidports.

5.. A hydraulic driving unit as claimedin claim 1 and valve meansoperable selectively to place said pumping means in communication withthe atmosphere or said fluid reservoir, means normally urging said valvein communication with said atmosphere to cause idling of said unitduring operation, andmeans for normally operating said valve to place itin communication with said fluid. reservoir to pass fluid therefrom tosaid impeller during operation of the latter to cause said driving unitto function in a driving capacity.

6. A hydraulic driving unitas claimed in claim 2 in which said web meansin said impeller comprises actuating plates carried by said impellereccentrically of saidpump rotor.

7. A hydraulic-driving unit as claimed in claim 1 in which the passagesformed in said impeller and said runner for passage of fluid provide aplurality of vane surfaces, said passages of said runner terminating indischarge ports, said closure means in connection with said runnercomprising a runner ring movable relatively to said runner and havingpassages normally registering with said ports, governor means connectedwith said runner ring for moving the latter as the runner speedincreases, finally to move said passages out of registry with saidports, said governor means including a plurality of pivotal weightedarms swingably mounted on the outside of said runner, spring meansnormally restraining movement of said arms and actuating means betweenthe runner ring and said arms, said spring means causing return movementof said arms and again establishing communication between said passagesof the runner ring and ports of the runner on reduction of speed of therunner to a given value.

8. A hydraulic driving unit as claimed in claim 1 in which the passagesformed in said impeller and said runner for passage of fluid provide aplurality of vane surfaces, said passages of said runner terminating indischarge ports, said closure means in connection with said runnercomprising a runner ring movable relatively to said runner and havingpassages normally registering with said ports, governor means connectedwith said runner ring for moving the latter as the runner speedincreases, finally to move said passages out of registry with saidports, said governor means including a plurality of rpivotal weightedarms swingably mounted on the outside of said runner, spring meansnormally restraining movement of said arms and actuating means betweenthe runner ring and said arms, said spring means causing return movementof said arms and again establishing communication between said passagesof the runner ring and ports of the runner on reduction of speed of therunner to a given value, said governor arms being connected to a controlring and operating collectively and uniformly.

9. A hydraulic driving unit as claimed in claim 1 in which the passagesformed in said impeller and said runner for passage of fluid provide aplurality of vane surfaces, said passages of said runner terminating indischarge ports, said closure means in connection with said runnercomprising a runner ring movable relatively to said runner and havingpassages normally registering with said ports, governor means connectedwith said runner ring for moving the latter as the runner speedincreases, finally to move said passages out of registry with saidports, said governor means including a plurality of pivotal weightedarms swingably mounted on the outside of said runner, spring meansnormally restraining movement of said arms and actuating means betweenthe runner ring and said arms, said spring means causing return movementof said arms and again establishing communication between said passagesof the runner ring and ports of the runner on reduction of speed of therunner to a given value, means for manually retracting said governorarms, said unit also including manually operable control means fordisconnecting said unit from a supply of operating fluid and placing itin communication with the atmosphere, said manual governor retractingmeans and the manual control means when operated respectively to retractsaid governor arms to cause said unit to communicate with the atmosphereproducing a free wheeling effect.

10. A hydraulic driving unit as claimed in claim 1 in which the impellerincludes a central web member, the passages of said impeller beingdisposed on opposite sides of the web member.

11. A hydraulic driving unit as claimed in claim 1 in which the runneris in the form of an annular vane structure comprised of a plurality ofsector-like elements including spring means exerting pressure betweenthe ends of said elements.

12. A hydraulic driving unit as claimed in claim 1 in which one of thepump components comprises a pump rotor having a (plurality of radialreciprocal blades, the other of said components comprising meansdisposed eccentrically of said blades and mounted on said impeller anddesigned to engage said blades of said pump rotor upon rotation of saidimpeller.

13. A hydraulic driving unit as claimed in claim 1 and progressivelyacting means for applying braking effect to said rotor.

14. A hydraulic driving unit as claimed in claim 2 and meanscommunicating said fluid reservoir with said pumping means including ahollow portion in said driven shaft placed in communication with saidpump rotor and connecting conduit means communicating with saidreservoir, and manually operable valve means for placing said shaft incommunication with said reservoir and alternatively with the atmosphere.

15. A hydraulic driving unit as claimed in claim 1 in which the passagesof said runner terminate outwardly in fluid discharge ports, said runnerincluding an annular runner vane structure adjacent its peripherymovable therewith and relatively thereto, said runner vane structurehaving a circumferential internal channel adapted to fit over andcircumferentially enclose outer portions of said impeller, said runnervane structure having a plurality of internal substantially radiallyextending passages intersecting said channel and providing a pluralityof vane surfaces, said runner vane structure also having dischargeorifices at its periphery communicating between said passage and saiddischarge ports of the runner, the passages of said impeller formingvane surfaces and designed to communicate with the passages of saidrunner vane structure and a distribution chamber within said fluiddriving unit communicating with the passages of said impeller and incommunication with said pumping means.

FRANK W. TORRANCE.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 1,062,876 Blymyer May 27, 19131,474,007 Sides Nov. 13, 1923 1,653,360 Howard Dec. 20, 1927 1,972,602Robbins Sept. 4, 1934 1,982,150 Bedford Nov. 27, 1934 2,067,457 MorganJan. 12, 1937 2,175,380 Dickson Oct. 10, 1939 2,195,561 Dickerson Apr.2, 1940 2,240,650 Heyer May 6, 1941 2,326,567 Root Aug. 10, 1943

